Planetary transmissions having one interconnecting member and an input member

ABSTRACT

The family of transmissions has a plurality of members that can be utilized in powertrains to provide at least eight forward speed ratios and one reverse speed ratio. The transmission family members include three planetary gear sets having seven torque-transmitting mechanisms and a fixed interconnection. The powertrain includes an engine and torque converter that is continuously connected to at least one of the planetary gear members and an output member that is continuously connected with another one of the planetary gear members. The seven torque-transmitting mechanisms provide interconnections between various gear members and with the transmission housing, and are operated in combinations of four to establish at least eight forward speed ratios and at least one reverse speed ratio.

TECHNICAL FIELD

The present invention relates to a family of power transmissions havingthree planetary gear sets that are controlled by seventorque-transmitting devices to provide at least eight forward speedratios and at least one reverse speed ratio.

BACKGROUND OF THE INVENTION

Passenger vehicles include a powertrain that is comprised of an engine,multi-speed transmission, and a differential or final drive. Themulti-speed transmission increases the overall operating range of thevehicle by permitting the engine to operate through its torque range anumber of times. The number of forward speed ratios that are availablein the transmission determines the number of times the engine torquerange is repeated. Early automatic transmissions had two speed ranges.This severely limited the overall speed range of the vehicle andtherefore required a relatively large engine that could produce a widespeed and torque range. This resulted in the engine operating at aspecific fuel consumption point during cruising, other than the mostefficient point. Therefore, manually-shifted (countershafttransmissions) were the most popular.

With the advent of three- and four-speed automatic transmissions, theautomatic shifting (planetary gear) transmission increased in popularitywith the motoring public. These transmissions improved the operatingperformance and fuel economy of the vehicle. The increased number ofspeed ratios reduces the step size between ratios and therefore improvesthe shift quality of the transmission by making the ratio interchangessubstantially imperceptible to the operator under normal vehicleacceleration.

It has been suggested that the number of forward speed ratios beincreased to six or more. Six-speed transmissions are disclosed in U.S.Pat. No. 4,070,927 issued to Polak on Jan. 31, 1978; and U.S. Pat. No.6,422,969 issued to Raghavan and Usoro on Jul. 23, 2002.

Six-speed transmissions offer several advantages over four- andfive-speed transmissions, including improved vehicle acceleration andimproved fuel economy. While many trucks employ power transmissionshaving six or more forward speed ratios, passenger cars are stillmanufactured with three- and four-speed automatic transmissions andrelatively few five or six-speed devices due to the size and complexityof these transmissions.

Seven-speed transmissions are disclosed in U.S. Pat. No. 6,623,397issued to Raghavan, Bucknor and Usoro. Eight speed transmissions aredisclosed in U.S. Pat. No. 6,425,841 issued to Haka. The Hakatransmission utilizes three planetary gear sets and six torquetransmitting devices, including two brakes and two clutches, to provideeight forward speed ratios and a reverse speed ratio. One of theplanetary gear sets is positioned and operated to establish two fixedspeed input members for the remaining two planetary gear sets. Seven-,eight- and nine-speed transmissions provide further improvements inacceleration and fuel economy over six-speed transmissions. However,like the six-speed transmissions discussed above, the development ofseven-, eight- and nine-speed transmissions has been precluded becauseof complexity, size and cost.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide an improved familyof transmissions having three planetary gear sets controlled to provideat least eight forward speed ratios and at least one reverse speedratio.

In one aspect of the present invention, the family of transmissions hasthree planetary gear sets, each of which includes a first, second andthird member, which members may comprise a sun gear, a ring gear, or aplanet carrier assembly member.

In referring to the first, second and third gear sets in thisdescription and in the claims, these sets may be counted “first” to“third” in any order in the drawings (i.e., left to right, right toleft, etc.). Additionally, the first, second or third members of eachgear set may be counted “first” to “third” in any order in the drawings(i.e., top to bottom, bottom to top, etc.) for each gear set.

In another aspect of the present invention, planet carrier assemblymembers of each of the planetary gear sets may be single pinion-carriersor double pinion-carriers.

In yet another aspect of the present invention, a first member of thefirst planetary gear set is continuously interconnected with a firstmember of the second planetary gear set through an interconnectingmember.

In yet a further aspect of the invention, each family memberincorporates an input shaft which is continuously connected with amember of the planetary gear sets and an output shaft which iscontinuously connected with another member of the planetary gear sets.

In still a further aspect of the invention, a first torque-transmittingmechanism, such as a clutch, selectively interconnects a first member ofthe third planetary gear set with a member of the first planetary gearset.

In another aspect of the invention, a second torque-transmittingmechanism, such as a clutch, selectively interconnects a second memberof the third planetary gear set with a member of the first or secondplanetary gear set.

In a still further aspect of the invention, a third torque-transmittingmechanism, such as a clutch, selectively interconnects a third member ofthe third planetary gear set with a member of the first or secondplanetary gear set.

In a still further aspect of the invention, a fourth torque-transmittingmechanism, such as a clutch, selectively interconnects a member of thefirst or second planetary gear set with another member of the first,second or third planetary gear set.

In a still further aspect of the invention, a fifth torque-transmittingmechanism, such as a brake, selectively interconnects a member of thefirst, second or third planetary gear set with a stationary member(transmission housing).

In still another aspect of the invention, a sixth torque-transmittingmechanism, such as a clutch, selectively interconnects a member of thesecond or third planetary gear set with another member of the first,second or third planetary gear set. Alternatively, a sixthtorque-transmitting mechanism, such as a brake, selectivelyinterconnects a member of the second or third planetary gear set withthe stationary member (transmission housing).

In still another aspect of the invention, a seventh torque-transmittingmechanism, such as a clutch, selectively interconnects a member of thefirst or second planetary gear set with another member of the first,second or third planetary gear set. Alternatively, the seventhtorque-transmitting mechanism, such as a brake, selectivelyinterconnects a member of the first or second planetary gear set withthe stationary member (transmission housing).

In still another aspect of the invention, the seven torque-transmittingmechanisms are selectively engageable in combinations of four to yieldat least eight forward speed ratios and at least one reverse speedratio.

The resulting transmission provides a significantly wider ratio spreadin comparison to transmissions with fewer speed ratios.

The above features and other features and advantages of the presentinvention are readily apparent from the following detailed descriptionof the best modes for carrying out the invention when taken inconnection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 a is a schematic representation of a powertrain including aplanetary transmission incorporating a family member of the presentinvention;

FIG. 1 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 1 a;

FIG. 2 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 2 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 2 a;

FIG. 3 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 3 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 3 a;

FIG. 4 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 4 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 4 a;

FIG. 5 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 5 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 5 a;

FIG. 6 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 6 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 6 a;

FIG. 7 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 7 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 7 a;

FIG. 8 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 8 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 8 a;

FIG. 9 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 9 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 9 a;

FIG. 10 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 10 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 10 a;

FIG. 11 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 11 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 11 a;

FIG. 12 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 12 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 12 a;

FIG. 13 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 13 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 13 a;

FIG. 14 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 14 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 14 a;

FIG. 15 a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention; and

FIG. 15 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 15 a.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring to the drawings, wherein like characters represent the same orcorresponding parts throughout the several views, there is shown in FIG.1 a a powertrain 10 having a conventional engine and torque converter12, a planetary transmission 14, and a conventional final drivemechanism 16.

The planetary transmission 14 includes an input shaft 17 continuouslyconnected with the engine and torque converter 12, a planetary geararrangement 18, and an output shaft 19 continuously connected with thefinal drive mechanism 16. The planetary gear arrangement 18 includesthree planetary gear sets 20, 30 and 40.

The planetary gear set 20 includes a sun gear member 22, a ring gearmember 24, and a planet carrier assembly member 26. The planet carrierassembly member 26 includes a plurality of pinion gears 27 rotatablymounted on a carrier member 29 and disposed in meshing relationship withboth the sun gear member 22 and the ring gear member 24.

The planetary gear set 30 includes a sun gear member 32, a ring gearmember 34, and a planet carrier assembly member 36. The planet carrierassembly member 36 includes a plurality of pinion gears 37 rotatablymounted on a carrier member 39 and disposed in meshing relationship withboth the sun gear member 32 and the ring gear member 34.

The planetary gear set 40 includes a sun gear member 42, a ring gearmember 44, and a planet carrier assembly member 46. The planet carrierassembly member 46 includes a plurality of pinion gears 47 rotatablymounted on a carrier member 49 and disposed in meshing relationship withboth the sun gear member 42 and the ring gear member 44.

The planetary gear arrangement also includes seven torque-transmittingmechanisms 50, 52, 54, 56, 57, 58 and 59. The torque-transmittingmechanisms 50, 52, 54 and 56 are rotating-type torque-transmittingmechanisms, commonly termed clutches. The torque-transmitting mechanisms57, 58 and 59 are stationary-type torque-transmitting mechanisms,commonly termed brakes or reaction clutches.

The input shaft 17 is continuously connected with the sun gear member42, and the output shaft 19 is continuously connected with the ring gearmember 24. The sun gear member 22 is continuously connected with thering gear member 34 through the interconnecting member 70.

The planet carrier assembly member 36 is selectively connectable withthe ring gear member 44 through the clutch 50. The sun gear member 32 isselectively connectable with the ring gear member 44 through the clutch52. The planet carrier assembly member 26 is selectively connectablewith the sun gear member 42 through the clutch 54. The planet carrierassembly member 26 is selectively connectable with the planet carrierassembly member 46 through the clutch 56. The planet carrier assemblymember 36 is selectively connectable with the transmission housing 60through the brake 57. The sun gear member 32 is selectively connectablewith the transmission housing 60 through the brake 58. The planetcarrier assembly member 46 is selectively connectable with thetransmission housing 60 through the brake 59.

As shown in FIG. 1 b, and in particular the truth table disclosedtherein, the torque-transmitting mechanisms are selectively engaged incombinations of four to provide eight forward speed ratios (as well asan extra sixth forward speed ratio (6′) and an extra seventh forwardspeed ratio (7′)) and a reverse speed ratio.

The reverse speed ratio is established with the engagement of theclutches 52 and 56, and the brakes 57 and 59. The clutch 52 connects thesun gear member 32 with the ring gear member 44, and the clutch 56connects the planet carrier assembly member 26 with the planet carrierassembly member 46. The brake 57 connects the planet carrier assemblymember 36 with the transmission housing 60. The brake 59 connects theplanet carrier assembly member 46 with the transmission housing 60. Thesun gear member 42 rotates at the same speed as the input shaft 17. Theplanet carrier assembly member 46 and the planet carrier assembly member26 do not rotate. The ring gear member 44 rotates at the same speed asthe sun gear member 32. The ring gear member 44 rotates at a speeddetermined from the speed of the sun gear member 42 and the ringgear/sun gear tooth ratio of the planetary gear set 40. The planetcarrier assembly member 36 does not rotate. The ring gear member 34rotates at the same speed as the sun gear member 22. The ring gearmember 34 rotates at a speed determined from the speed of the sun gearmember 32 and the ring gear/sun gear tooth ratio of the planetary gearset 30. The ring gear member 24 rotates at the same speed as the outputshaft 19. The ring gear member 24, and therefore the output shaft 19,rotates at a speed determined from the speed of the sun gear member 22and the ring gear/sun gear tooth ratio of the planetary gear set 20. Thenumerical value of the reverse speed ratio is determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 20, 30 and40.

The first forward speed ratio is established with the engagement of theclutches 50, 52, and 56, and the brake 59. The clutch 50 connects theplanet carrier assembly member 36 with the ring gear member 44. Theclutch 52 connects the sun gear member 32 with the ring gear member 44.The clutch 56 connects the planet carrier assembly member 26 with theplanet carrier assembly member 46. The brake 59 connects the planetcarrier assembly member 46 with the transmission housing 60. The sungear member 42 rotates at the same speed as the input shaft 17. Theplanet carrier assembly member 46 and the planet carrier assembly member26 do not rotate. The ring gear member 44 and the planetary gear set 30rotate at the same speed as the sun gear member 22. The ring gear member44 rotates at a speed determined from the speed of the sun gear member42 and the ring gear/sun gear tooth ratio of the planetary gear set 40.The ring gear member 24 rotates at the same speed as the output shaft19. The ring gear member, and therefore the output shaft 19, rotates ata speed determined from the speed of the sun gear member 22 and the ringgear/sun gear tooth ratio of the planetary gear set 20. The numericalvalue of the first forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 20 and 40.

The second forward speed ratio is established with the engagement of theclutches 50 and 56, and the brakes 58 and 59. The clutch 50 connects theplanet carrier assembly member 36 with the ring gear member 44. Theclutch 56 connects the planet carrier assembly member 26 with the planetcarrier assembly member 46. The brake 58 connects the sun gear member 32with the transmission housing 60. The brake 59 connects the planetcarrier assembly member 46 with the transmission housing 60. The sungear member 42 rotates at the same speed as the input shaft 17. Theplanet carrier assembly member 46 and the planet carrier assembly member26 do not rotate. The ring gear member 44 rotates at the same speed asthe planet carrier assembly member 36. The ring gear member 44 rotatesat a speed determined from the speed of the sun gear member and the ringgear/sun gear tooth ratio of the planetary gear set 40. The sun gearmember 32 does not rotate. The ring gear member 34 rotates at the samespeed as the sun gear member 22. The ring gear member 34 rotates at aspeed determined from the speed of the planet carrier assembly member 36and the ring gear/sun gear tooth ratio of the planetary gear set 30. Thering gear member 24 rotates at the same speed as the output shaft 19.The ring gear member 24, and therefore the output shaft 19, rotates at aspeed determined from the speed of the sun gear member 22 and the ringgear/sun gear tooth ratio of the planetary gear set 20. The numericalvalue of the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 20, 30 and 40.

The third forward speed ratio is established with the engagement of theclutches 50 and 56, and the brakes 57 and 58. The clutch 50 connects theplanet carrier assembly member 36 with the ring gear member 44. Theclutch 56 connects the planet carrier assembly member 26 with the planetcarrier assembly member 46. The brake 57 connects the planet carrierassembly member 36 with the transmission housing 60. The brake 58connects the sun gear member 32 with the transmission housing 60. Thesun gear member 42 rotates at the same speed as the input shaft 17. Theplanet carrier assembly member 46 rotates at the same speed as theplanet carrier assembly member 26. The ring gear member 44, theplanetary gear set 30 and the sun gear member 22 do not rotate. Theplanet carrier assembly member 46 rotates at a speed determined from thespeed of the sun gear member 42 and the ring gear/sun gear tooth ratioof the planetary gear set 40. The ring gear member 24 rotates at thesame speed as the output shaft 19. The ring gear member 24, andtherefore the output shaft 19, rotates at a speed determined from thespeed of the planet carrier assembly member 26 and the ring gear/sungear tooth ratio of the planetary gear set 20. The numerical value ofthe third forward speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 20 and 40.

The fourth forward speed ratio is established with the engagement of theclutches 50, 54 and 56, and the brake 58. The clutch 50 connects theplanet carrier assembly member 36 with the ring gear member 44. Theclutch 54 connects the planet carrier assembly member 26 with the sungear member 42. The clutch 56 connects the planet carrier assemblymember 26 with the planet carrier assembly member 46. The brake 58connects the sun gear member 32 with the transmission housing 60. Theplanetary gear set 40, the planet carrier assembly member 36 and theplanet carrier assembly member 26 rotate at the same speed as the inputshaft 17. The sun gear member 32 does not rotate. The ring gear member34 rotates at the same speed as the sun gear member 22. The ring gearmember 34 rotates at a speed determined from the speed of the planetarygear set 36 and the ring gear/sun gear tooth ratio of the planetary gearset 30. The ring gear member 24 rotates at the same speed as the outputshaft 19. The ring gear member 24, and therefore the output shaft 19,rotates at a speed determined from the speed of the planet carrierassembly member 26, the speed of the sun gear member 22 and the ringgear/sun gear tooth ratio of the planetary gear set 20. The numericalvalue of the fourth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 20 and 30.

The fifth forward speed ratio is established with the engagement of theclutches 50, 52, 54 and 56. In this configuration, the input shaft 17 isdirectly connected with the output shaft 19. The numerical value of thefifth forward speed ratio is 1.

The extra sixth forward speed ratio (6′) is established with theengagement of the clutches 52 and 54, and the brakes 57 and 59. Theclutch 52 connects the sun gear member 32 with the ring gear member 44.The clutch 54 connects the planet carrier assembly member 26 with thesun gear member 32. The brake 57 connects the planet carrier assemblymember 36 with the transmission housing 60. The brake 59 connects theplanet carrier assembly member 46 with the transmission housing 60. Thesun gear member 42 and the planet carrier assembly member 26 rotate atthe same speed as the input shaft 17. The planet carrier assembly member46 does not rotate. The ring gear member 44 rotates at the same speed asthe sun gear member 32. The ring gear member 44 rotates at a speeddetermined from the speed of the sun gear member 42 and the ringgear/sun gear tooth ratio of the planetary gear set 40. The planetcarrier assembly member 36 does not rotate. The ring gear member 34rotates at the same speed as the sun gear member 22. The ring gearmember 34 rotates at a speed determined from the speed of the sun gearmember 32 and the ring gear/sun gear tooth ratio of the planetary gearset 30. The ring gear member 24 rotates at the same speed as the outputshaft 19. The ring gear member 24, and therefore the output shaft 19,rotates at a speed determined from the speed of the planet carrierassembly member 26, the speed of the sun gear member 22 and the ringgear/sun gear tooth ratio of planetary gear set 20. The numerical valueof the extra sixth forward speed ratio (6′) is determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 20, 30 and40.

The sixth forward speed ratio is established with the engagement of theclutches 50, 52, and 54, and the brake 58. The clutch 50 connects theplanet carrier assembly member 36 with the ring gear member 44. Theclutch 52 connects the sun gear member 32 with the ring gear member 44.The clutch 54 connects the planet carrier assembly member 26 with thesun gear member 42. The brake 58 connects the sun gear member 32 withthe transmission housing 60. The sun gear member 42 and the planetcarrier assembly member 26 rotate at the same speed as the input shaft17. The ring gear member 44, the planetary gear set 30 and the sun gearmember 22 do not rotate. The ring gear member 24 rotates at the samespeed as the output shaft 19. The ring gear member 24, and therefore theoutput shaft 19, rotates at a speed determined from the speed of theplanet carrier assembly member 26 and the ring gear/sun gear tooth ratioof the planetary gear set 20. The numerical value of the sixth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratioof the planetary gear set 20.

The seventh forward speed ratio is established with the engagement ofthe clutches 50, 52, and 54, and the brake 59. The clutch 50 connectsthe planet carrier assembly member 36 with the ring gear member 44. Theclutch 52 connects the sun gear member 32 with the ring gear member 44.The clutch 54 connects the planet carrier assembly member 26 with thesun gear member 42. The brake 59 connects the planet carrier assemblymember 46 with the transmission housing 60. The sun gear member 42 andthe planet carrier assembly member 26 rotate at the same speed as theinput shaft 17. The planet carrier assembly member 46 does not rotate.The ring gear member 44 and the planetary gear set 30 rotate at the samespeed as the sun gear member 22. The ring gear member 44 rotates at aspeed determined from the speed of the sun gear member 42 and the ringgear/sun gear tooth ratio of the planetary gear set 40. The ring gearmember 24 rotates at the same speed as the output shaft 19. The ringgear member 24, and therefore the output shaft 19, rotates at a speeddetermined from the speed of the planet carrier assembly member 26, thespeed of the sun gear member 22 and the ring gear/sun gear tooth ratioof the planetary gear set 20. The numerical value of the seventh forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 20 and 40.

The extra seventh forward speed ratio (7′) is established with theengagement of the clutches 52, 54, and 56, and the brake 57. The clutch52 connects the sun gear member 32 with the ring gear member 44. Theclutch 54 connects the planet carrier assembly member 26 with the sungear member 42. The clutch 56 connects the planet carrier assemblymember 26 with the planet carrier assembly member 46. The brake 57connects the planet carrier assembly member 36 with the transmissionhousing 60. The planetary gear set 40, the sun gear member 32 and theplanet carrier assembly member 26 rotate at the same speed as the inputshaft 17. The planet carrier assembly member 36 does not rotate. Thering gear member 34 rotates at the same speed as the sun gear member 22.The ring gear member 34 rotates at a speed determined from the speed ofthe sun gear member 32 and the ring gear/sun gear tooth ratio of theplanetary gear set 30. The ring gear member 24 rotates at the same speedas the output shaft 19. The ring gear member 24, and therefore theoutput shaft 19, rotates at a speed determined from the speed of theplanet carrier assembly member 26, the speed of the sun gear member 22,and the ring gear/sun gear tooth ratio of the planetary gear set 20. Thenumerical value of the extra seventh forward speed ratio (7′) isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 20 and 30.

The eighth forward speed ratio is established with the engagement of theclutches 50 and 54, and the brakes 58 and 59. The clutch 50 connects theplanet carrier assembly member 26 with the ring gear member 44. Theclutch 54 connects the planet carrier assembly member 26 with the sungear member 42. The brake 58 connects the sun gear member 32 with thetransmission housing 60. The brake 59 connects the planet carrierassembly member 46 with the transmission housing 60. The sun gear member42 and the planet carrier assembly member 26 rotate at the same speed asthe input shaft 17. The planet carrier assembly member 46 does notrotate. The ring gear member 44 rotates at the same speed as the planetcarrier assembly member 36. The ring gear member 44 rotates at a speeddetermined from the speed of the sun gear member 42 and the ringgear/sun gear tooth ratio of the planetary gear set 40. The sun gearmember 32 does not rotate. The ring gear member 34 rotates at the samespeed as the sun gear member 22. The ring gear member 34 rotates at aspeed determined from the speed of the planet carrier assembly member 36and the ring gear/sun gear tooth ratio of the planetary gear set 30. Thering gear member 24 rotates at the same speed as the output shaft 19.The ring gear 24, and therefore the output shaft 19, rotates at a speeddetermined from the speed of the planet carrier assembly member 26, thespeed of the sun gear member 22 and the ring gear/sun gear tooth ratioof the planetary gear set 20. The numerical value of the eighth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 20, 30 and 40.

As set forth above, the engagement schedule for the torque-transmittingmechanisms is shown in the truth table of FIG. 1 b. This truth tablealso provides an example of speed ratios that are available utilizingthe ring gear/sun gear tooth ratios given by way of example in FIG. 1 b.The N_(R1)/S_(R1) value is the tooth ratio of the planetary gear set 20;the N_(R2)/S_(R2) value is the tooth ratio of the planetary gear set 30;and the N_(R3)/S_(R3) value is the tooth ratio of the planetary gear set40. Also, the chart of FIG. 1 b describes the ratio steps that areattained utilizing the sample of tooth ratios given. For example, thestep ratio between the first and second forward speed ratios is 1.50,while the step ratio between the reverse speed ratio and first forwardratio is −2.00. It should be noted that the single step forward ratiointerchanges are of the single transition variety. Additionally, thetorque-transmitting mechanisms 52, 56 and 59 remain engaged through theneutral condition, thereby simplifying the forward/reverse interchange.

FIG. 2 a shows a powertrain 110 having a conventional engine and torqueconverter 12, a planetary transmission 114, and a conventional finaldrive mechanism 16.

The planetary transmission 114 includes an input shaft 17 continuouslyconnected with the engine and torque converter 12, a planetary geararrangement 118, and an output shaft 19 continuously connected with thefinal drive mechanism 16. The planetary gear arrangement 118 includesthree planetary gear sets 120, 130 and 140.

The planetary gear set 120 includes a sun gear member 122, a ring gearmember 124, and a planet carrier assembly member 126. The planet carrierassembly member 126 includes a plurality of pinion gears 127 rotatablymounted on a carrier member 129 and disposed in meshing relationshipwith both the sun gear member 122 and the ring gear member 124.

The planetary gear set 130 includes a sun gear member 132, a ring gearmember 134, and a planet carrier assembly member 136. The planet carrierassembly member 136 includes a plurality of pinion gears 137 rotatablymounted on a carrier member 139 and disposed in meshing relationshipwith both the sun gear member 132 and the ring gear member 134.

The planetary gear set 140 includes a sun gear member 142, a ring gearmember 144, and a planet carrier assembly member 146. The planet carrierassembly member 146 includes a plurality of pinion gears 147 rotatablymounted on a carrier member 149 and disposed in meshing relationshipwith both the sun gear member 142 and the ring gear member 144.

The planetary gear arrangement 118 also includes seventorque-transmitting mechanisms 150, 152, 154, 156, 157, 158 and 159. Thetorque-transmitting mechanisms 150, 152, 154, 156 and 157 arerotating-type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanisms 158 and 159 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member142, and the output shaft 19 is continuously connected with the ringgear member 124. The sun gear member 122 is continuously connected withthe ring gear member 134 through the interconnecting member 170. Theinterconnecting member 170 may be one component or separate components.

The sun gear member 122 is selectively connectable with the ring gearmember 144 through the clutch 150. The sun gear member 122 isselectively connectable with the planet carrier assembly member 146through the clutch 152. The planet carrier assembly member 126 isselectively connectable with the planet carrier assembly member 136through the clutch 154. The planet carrier assembly member 136 isselectively connectable with the ring gear member 144 through the clutch156. The planet carrier assembly member 126 is selectively connectablewith the sun gear member 142 through the clutch 157. The sun gear member132 is selectively connectable with the transmission housing 160 throughthe brake 158. The ring gear member 144 is selectively connectable withthe transmission housing 160 through the brake 159.

The truth table of FIG. 2 b describes the engagement sequence utilizedto provide eight forward speed ratios and a reverse speed ratio in theplanetary gear arrangement 118 shown in FIG. 2 a.

The truth tables given in FIGS. 2 b, 3 b, 4 b, Sb, 6 b, 7 b, 8 b, 9 b,10 b, 11 b, 12 b, 13 b, 14 b, 15 b and 16 b show the engagementsequences for the torque-transmitting mechanisms to provide at leasteight forward speed ratios and at least one reverse ratio. As shown anddescribed above for the configuration in FIG. 1 a, those skilled in theart will understand from the respective truth tables how the speedratios are established through the planetary gear sets identified in thewritten description.

The truth table of FIG. 2 b also provides an example of the ratios thatcan be attained with the family members shown in FIG. 2 a utilizing thesample tooth ratios given in FIG. 2 b. The N_(R1)/S_(R1) value is thetooth ratio of the planetary gear set 120; the N_(R2)/S_(R2) value isthe tooth ratio of the planetary gear set 130; and the N_(R3)/S_(R3)value is the tooth ratio of the planetary gear set 140. Also shown inFIG. 2 b are the ratio steps between single step ratios in the forwarddirection as well as the reverse to first ratio step. For example, thefirst to second step ratio is 1.86. The torque-transmitting mechanisms152 and 159 remain engaged through the neutral condition, thussimplifying the forward/reverse interchange.

Turning to FIG. 3 a, a powertrain 210 includes the engine and torqueconverter 12, a planetary transmission 214, and a final drive mechanism16. The planetary transmission 214 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 218, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 218 includes three planetary gear sets 220, 230 and 240.

The planetary gear set 220 includes a sun gear member 222, a ring gearmember 224, and a planet carrier assembly member 226. The planet carrierassembly member 226 includes a plurality of pinion gears 227 rotatablymounted on a carrier member 229 and disposed in meshing relationshipwith both the sun gear member 222 and the ring gear member 224.

The planetary gear set 230 includes a sun gear member 232, a ring gearmember 234, and a planet carrier assembly member 236. The planet carrierassembly member 236 includes a plurality of pinion gears 237 rotatablymounted on a carrier member 239 and disposed in meshing relationshipwith both the sun gear member 232 and the ring gear member 234.

The planetary gear set 240 includes a sun gear member 242, a ring gearmember 244, and a planet carrier assembly member 246. The planet carrierassembly member 246 includes a plurality of pinion gears 247 rotatablymounted on a carrier member 249 and disposed in meshing relationshipwith both the sun gear member 242 and the ring gear member 244.

The planetary gear arrangement 218 also includes seventorque-transmitting mechanisms 250, 252, 254, 256, 257, 258 and 259. Thetorque-transmitting mechanisms 250, 252, 254, 256 and 257 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 258 and 259 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member242, and the output shaft 19 is continuously connected with the planetcarrier assembly member 226. The planet carrier assembly member 226 iscontinuously connected with the ring gear member 234 through theinterconnecting member 270.

The ring gear member 224 is selectively connectable with the planetcarrier assembly member 236 through the clutch 250. The ring gear member224 is selectively connectable with the ring gear member 244 through theclutch 252. The planet carrier assembly member 236 is selectivelyconnectable with the sun gear member 242 through the clutch 254. The sungear member 232 is selectively connectable with the ring gear member 244through the clutch 256. The sun gear member 232 is selectivelyconnectable with the planet carrier assembly member 246 through theclutch 257. The sun gear member 222 is selectively connectable with thetransmission housing 260 through the brake 258. The planet carrierassembly member 246 is selectively connectable with the transmissionhousing 260 through the brake 259.

As shown in the truth table in FIG. 3 b, the torque-transmittingmechanisms are engaged in combinations of four to establish eightforward speed ratios (as well as an extra fifth forward speed ratio(5′)) and a reverse ratio.

The truth table of FIG. 3 b also provides an example of speed ratiosthat are available with the family member described above. Theseexamples of speed ratios are determined utilizing the tooth ratios givenin FIG. 3 b. The N_(R1)/S_(R1) value is the tooth ratio of the planetarygear set 220; the N_(R1)/S_(R1) value is the tooth ratio of theplanetary gear set 230; and the N_(R3)/S_(R3) value is the tooth ratioof the planetary gear set 240. Also depicted in FIG. 3 b is a chartrepresenting the ratio steps between adjacent forward speed ratios andthe reverse speed ratio. For example, the first to second ratiointerchange has a step of 1.72. It can also be readily determined fromthe truth table of FIG. 3 b that all of the single step forward ratiointerchanges are of the single transition variety. Additionally, thetorque-transmitting mechanisms 250, 257 and 259 remain engaged throughthe neutral condition, thus simplifying the forward/reverse interchange.

A powertrain 310, shown in FIG. 4 a, includes the engine and torqueconverter 12, a planetary transmission 314, and the final drivemechanism 16. The planetary transmission 314 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 318, and output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 318 includes three planetary gear sets 320, 330 and 340.

The planetary gear set 320 includes a sun gear member 322, a ring gearmember 324, and a planet carrier assembly member 326. The planet carrierassembly member 326 includes a plurality of pinion gears 327 rotatablymounted on a carrier member 329 and disposed in meshing relationshipwith both the sun gear member 322 and the ring gear member 324.

The planetary gear set 330 includes a sun gear member 332, a ring gearmember 334, and a planet carrier assembly member 336. The planet carrierassembly member 336 includes a plurality of pinion gears 337 rotatablymounted on a carrier member 339 and disposed in meshing relationshipwith both the sun gear member 332 and the ring gear member 334.

The planetary gear set 340 includes a sun gear member 342, a ring gearmember 344, and a planet carrier assembly member 346. The planet carrierassembly member 346 includes a plurality of pinion gears 347 rotatablymounted on a carrier member 349 and disposed in meshing relationshipwith both the sun gear member 342 and the ring gear member 344.

The planetary gear arrangement 318 also includes seventorque-transmitting mechanisms 350, 352, 354, 356, 357, 358 and 359. Thetorque-transmitting mechanisms 350, 352, 354 and 356 are rotating typetorque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 357, 358 and 359 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member322, and the output shaft 19 is continuously connected with the ringgear member 344. The ring gear member 324 is continuously connected withthe sun gear member 332 through the interconnecting member 370.

The sun gear member 322 is selectively connectable with the planetcarrier assembly member 346 through the clutch 350. The planet carrierassembly member 326 is selectively connectable with the sun gear member342 through the clutch 352. The ring gear member 334 is selectivelyconnectable with the planet carrier assembly member 346 through theclutch 354. The planet carrier assembly member 336 is selectivelyconnectable with the sun gear member 342 through the clutch 356. Thering gear member 324 is selectively connectable with the transmissionhousing 360 through the brake 357. The planet carrier assembly member326 is selectively connectable with the transmission housing 360 throughthe brake 358. The ring gear member 334 is selectively connectable withthe transmission housing 360 through the brake 359.

The truth table shown in FIG. 4 b describes the engagement combinationand the engagement sequence necessary to provide a reverse drive ratioand nine forward speed ratios (as well as an extra eighth forward speedratio (8′) and an extra ninth forward speed ratio (9′)). A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 4 b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 4 b. The N_(R1)/S_(R1) value is thetooth ratio for the planetary gear set 320; the N_(R1)/S_(R1) value isthe tooth ratio for the planetary gear set 330; and the N_(R3)/S_(R3)value is the tooth ratio for the planetary gear set 340. Also given inFIG. 4 b is a chart describing the step ratios between the adjacentforward speed ratios and the reverse to first forward speed ratio. Forexample, the first to second forward speed ratio step is 1.85. It can bereadily determined from the truth table of FIG. 4 b that each of theforward single step ratio interchanges is a single transition shift.Additionally, the torque-transmitting mechanisms 354 and 359 remainengaged through the neutral condition, thus simplifying theforward/reverse interchange.

A powertrain 410, shown in FIG. 5 a, includes the engine and torqueconverter 12, a planetary transmission 414 and the final drive mechanism16. The planetary transmission 414 includes a planetary gear arrangement418, input shaft 17 and output shaft 19. The planetary gear arrangement418 includes three simple planetary gear sets 420, 430 and 440.

The planetary gear set 420 includes a sun gear member 422, a ring gearmember 424, and a planet carrier assembly member 426. The planet carrierassembly member 426 includes a plurality of pinion gears 427 rotatablymounted on a carrier member 429 and disposed in meshing relationshipwith both the sun gear member 422 and the ring gear member 424.

The planetary gear set 430 includes a sun gear member 432, a ring gearmember 434, and a planet carrier assembly member 436. The planet carrierassembly member 436 includes a plurality of pinion gears 437 rotatablymounted on a carrier member 439 and disposed in meshing relationshipwith both the sun gear member 432 and the ring gear member 434.

The planetary gear set 440 includes a sun gear member 442, a ring gearmember 444, and a planet carrier assembly member 446. The planet carrierassembly member 446 includes a plurality of pinion gears 447 rotatablymounted on a carrier member 449 and disposed in meshing relationshipwith both the sun gear member 442 and the ring gear member 444.

The planetary gear arrangement 418 also includes seventorque-transmitting mechanisms 450, 452, 454, 456, 457, 458 and 459. Thetorque-transmitting mechanisms 450, 452, 454, 456 and 457 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 458 and 459 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member432, and the output shaft 19 is continuously connected with the ringgear member 424. The sun gear member 422 is continuously connected withthe planet carrier assembly member 436 through the interconnectingmember 470. The interconnecting member 470 may be one component orseparate components.

The sun gear member 422 is selectively connectable with the planetcarrier assembly member 446 through the clutch 450. The planet carrierassembly member 426 is selectively connectable with the sun gear member432 through the clutch 452. The ring gear member 434 is selectivelyconnectable with the sun gear member 442 through the clutch 454. Theplanet carrier assembly member 426 is selectively connectable with thering gear member 444 through the clutch 456. The ring gear member 424 isselectively connectable with the ring gear member 444 through the clutch457. The planet carrier assembly member 446 is selectively connectablewith the transmission housing 460 through the brake 458. The sun gearmember 442 is selectively connectable with the transmission housing 460through the brake 459.

The truth table shown in FIG. 5 b describes the engagement combinationand sequence of the torque-transmitting mechanisms 450, 452, 454, 456,457; 458 and 459 that are employed to provide a reverse drive ratio andnine forward speed ratios, as well as an extra third forward speed ratio(3′), an extra sixth forward speed ratio (6′) and an extra ninth forwardspeed ratio (9′).

Also given in the truth table of FIG. 5 b is a set of numerical valuesthat are attainable with the present invention utilizing the ringgear/sun gear tooth ratios shown. The N_(R1)/S_(R1) value is the toothratio of the planetary gear set 420; the N_(R2)/S_(R2) value is thetooth ratio of the planetary gear set 430; and the N_(R3)/S_(R3) valueis the tooth ratio of the planetary gear set 440. As can also bedetermined from the truth table of FIG. 5 b, all of the single stepforward interchanges are of the single transition variety. Additionally,the torque-transmitting mechanisms 454, 456 and 458 remain engagedthrough the neutral condition, thus simplifying the forward/reverseinterchange.

FIG. 5 b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse ratio and first forward ratio.For example, the ratio step between the first and second forward ratiosis 1.74.

A powertrain 510, shown in FIG. 6 a, includes an engine and torqueconverter 12, a planetary gear transmission 514 and the final drivemechanism 16. The planetary transmission 514 includes the input shaft17, a planetary gear arrangement 518 and the output shaft 19. Theplanetary gear arrangement 518 includes three planetary gear sets 520,530 and 540.

The planetary gear set 520 includes a sun gear member 522, a ring gearmember 524, and a planet carrier assembly member 526. The planet carrierassembly member 526 includes a plurality of pinion gears 527 rotatablymounted on a carrier member 529 and disposed in meshing relationshipwith both the sun gear member 522 and the ring gear member 524.

The planetary gear set 530 includes a sun gear member 532, a ring gearmember 534, and a planet carrier assembly member 536. The planet carrierassembly member 536 includes a plurality of pinion gears 537 rotatablymounted on a carrier member 539 and disposed in meshing relationshipwith both the sun gear member 532 and the ring gear member 534.

The planetary gear set 540 includes a sun gear member 542, a ring gearmember 544, and a planet carrier assembly member 546. The planet carrierassembly member 546 includes a plurality of pinion gears 547 rotatablymounted on a carrier member 549 and disposed in meshing relationshipwith both the sun gear member 542 and the ring gear member 544.

The planetary gear arrangement 518 also includes seventorque-transmitting mechanisms 550, 552, 554, 556, 557, 558 and 559. Thetorque-transmitting mechanisms 550, 552, 554, 556 and 557 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 558 and 559 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member522, and the output shaft 19 is continuously connected with the ringgear member 544. The planet carrier assembly member 526 is continuouslyconnected with the ring gear member 534 through the interconnectingmember 570.

The planet carrier assembly member 526 is selectively connectable withthe sun gear member 542 through the clutch 550. The sun gear member 522is selectively connectable with the sun gear member 542 through theclutch 552. The sun gear member 522 is selectively connectable with theplanet carrier assembly member 546 through the clutch 554. The ring gearmember 524 is selectively connectable with the planet carrier assemblymember 536 through the clutch 556. The planet carrier assembly member536 is selectively connectable with the planet carrier assembly member546 through the clutch 557. The planet carrier assembly member 536 isselectively connectable with the transmission housing 560 through thebrake 558. The sun gear member 532 is selectively connectable with thetransmission housing 560 through the brake 559.

The truth table shown in FIG. 6 b describes the engagement sequence andcombination of the torque-transmitting mechanisms to provide a reversespeed ratio (Reverse), an extra reverse speed ratio (Reverse′), andeight forward speed ratios. It should be noted that thetorque-transmitting mechanism 557 remains engaged through the neutralcondition, thereby simplifying the forward/reverse interchange. Also,each of the single step forward ratio interchanges is of the singletransmission type. The chart of FIG. 6 b describes the ratio stepsbetween adjacent forward speed ratios and the ratio step between thereverse and first forward speed ratio.

The sample speed ratios given in the truth table are determinedutilizing the tooth ratio values also given in FIG. 6 b. TheN_(R1)/S_(R1) value is the tooth ratio of the planetary gear set 520;the N_(R2)/S_(R2) value is the tooth ratio of the planetary gear set530; and the N_(R3)/S_(R3) value is the tooth ratio of the planetarygear set 540.

A powertrain 610, shown in FIG. 7 a, has the engine and torque converter12, a planetary transmission 614 and the final drive mechanism 16. Theplanetary transmission 614 includes the input shaft 17, a planetary geararrangement 618 and the output shaft 19. The planetary gear arrangement618 includes three planetary gear sets 620, 630 and 640.

The planetary gear set 620 includes a sun gear member 622, a ring gearmember 624, and a planet carrier assembly member 626. The planet carrierassembly member 626 includes a plurality of pinion gears 627 rotatablymounted on a carrier member 629 and disposed in meshing relationshipwith both the sun gear member 622 and the ring gear member 624.

The planetary gear set 630 includes a sun gear member 632, a ring gearmember 634, and a planet carrier assembly member 636. The planet carrierassembly member 636 includes a plurality of pinion gears 637 rotatablymounted on a carrier member 639 and disposed in meshing relationshipwith both the sun gear member 632 and the ring gear member 634.

The planetary gear set 640 includes a sun gear member 642, a ring gearmember 644, and a planet carrier assembly member 646. The planet carrierassembly member 646 includes a plurality of pinion gears 647 rotatablymounted on a carrier member 649 and disposed in meshing relationshipwith both the sun gear member 642 and the ring gear member 644.

The planetary gear arrangement 618 also includes seventorque-transmitting mechanisms 650, 652, 654, 656, 657, 658 and 659. Thetorque-transmitting mechanisms 650, 652, 654, 656 and 657 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 658 and 659 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member642, and the output shaft 19 is continuously connected with the planetcarrier assembly member 636. The ring gear member 624 is continuouslyconnected with the sun gear member 632 through the interconnectingmember 670. The interconnecting member 670 may be one component orseparate components.

The sun gear member 622 is selectively connectable with the planetcarrier assembly member 646 through the clutch 650. The planet carrierassembly member 626 is selectively connectable with the planet carrierassembly member 636 through the clutch 652. The planet carrier assemblymember 626 is selectively connectable with the ring gear member 644through the clutch 654. The ring gear member 634 is selectivelyconnectable with the planet carrier assembly member 646 through theclutch 656. The ring gear member 634 is selectively connectable with thering gear member 644 through the clutch 657. The ring gear member 624 isselectively connectable with the transmission housing 660 through thebrake 658. The sun gear member 622 is selectively connectable with thetransmission housing 660 through the brake 659.

The truth table shown in FIG. 7 b describes the combination oftorque-transmitting mechanism engagements that will provide the areverse (Reverse) drive ratio and eight forward speed ratios (as well asan extra second forward speed ratio (2′), an extra third forward speedratio (3′), an extra eighth forward speed ratio (8′) and three extrareverse speed ratios (Reverse′, Reverse″ and Reverse′″)), and thesequence of these engagements and interchanges.

The ratio values given are by way of example and are establishedutilizing the ring gear/sun gear tooth ratios given in FIG. 7 b. Forexample, the N_(R1)/S_(R1) value is the tooth ratio of the planetarygear set 620; the N_(R1)/S_(R2) value is the tooth ratio of theplanetary gear set 630; and the N_(R3)/S_(R3) value is the tooth ratioof the planetary gear set 640. The ratio steps between adjacent forwardratios and the reverse (Reverse) to first ratio are also given in FIG. 7b. For example, the ratio step between the first and second forwardratio is 1.44. As can also be determined from the truth table of FIG. 7b, each of the single step forward interchanges is of the singletransition variety. Additionally, the torque-transmitting mechanisms650, 654 and 658 remain engaged through the neutral condition, thussimplifying the forward/reverse interchange.

A powertrain 710, shown in FIG. 8 a, has the conventional engine andtorque converter 12, a planetary transmission 714, and the conventionalfinal drive mechanism 16. The engine and torque converter 12 aredrivingly connected with the planetary transmission 714 through theinput shaft 17. The planetary transmission 714 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 714 includes a planetary gear arrangement 718that has a first planetary gear set 720, a second planetary gear set730, and a third planetary gear set 740.

The planetary gear set 720 includes a sun gear member 722, a ring gearmember 724, and a planet carrier assembly member 726. The planet carrierassembly member 726 includes a plurality of pinion gears 727 rotatablymounted on a carrier member 729 and disposed in meshing relationshipwith both the sun gear member 722 and the ring gear member 724.

The planetary gear set 730 includes a sun gear member 732, a ring gearmember 734, and a planet carrier assembly member 736. The planet carrierassembly member 736 includes a plurality of pinion gears 737 rotatablymounted on a carrier member 739 and disposed in meshing relationshipwith both the sun gear member 732 and the ring gear member 734.

The planetary gear set 740 includes a sun gear member 742, a ring gearmember 744, and a planet carrier assembly member 746. The planet carrierassembly member 746 includes a plurality of pinion gears 747 rotatablymounted on a carrier member 749 and disposed in meshing relationshipwith both the sun gear member 742 and the ring gear member 744.

The planetary gear arrangement 718 also includes seventorque-transmitting mechanisms 750, 752, 754, 756, 757, 758 and 759. Thetorque-transmitting mechanisms 750, 752, 754, 756 and 757 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 758 and 759 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member742, and the output shaft 19 is continuously connected with the ringgear member 724. The sun gear member 722 is continuously connected withthe ring gear member 734 through the interconnecting member 770. Theinterconnecting member 770 may be one component or separate components.

The ring gear member 734 is selectively connectable with the planetcarrier assembly member 746 through the clutch 750. The planet carrierassembly member 726 is selectively connectable with the planet carrierassembly member 736 through the clutch 752. The planet carrier assemblymember 736 is selectively connectable with the ring gear member 744through the clutch 754. The planet carrier assembly member 726 isselectively connectable with the sun gear member 742 through the clutch756. The planet carrier assembly member 726 is selectively connectablewith the planet carrier assembly member 746 through the clutch 757. Thesun gear member 732 is selectively connectable with the transmissionhousing 760 through the brake 758. The planet carrier assembly member746 is selectively connectable with the transmission housing 760 throughthe brake 759.

The truth table of FIG. 8 b defines the torque-transmitting mechanismengagement sequence utilized for each of the nine forward speed ratiosand a reverse speed ratio, as well as an extra third forward speed ratio(3′) and an extra fourth forward speed ratio (4′). Also given in thetruth table is a set of numerical values that are attainable with thepresent invention utilizing the ring gear/sun gear tooth ratios given inFIG. 8 b. The N_(R1)/S_(R1) value is the tooth ratio of the planetarygear set 720; the N_(R2)/S_(R2) value is the tooth ratio of theplanetary gear set 730; and the N_(R3)/S_(R3) value is the tooth ratioof the planetary gear set 740. As may be determined from the truth tableof FIG. 8 b, the torque-transmitting mechanisms 750, 752 and 759 remainengaged through the neutral condition, thus simplifying theforward/reverse interchange.

FIG. 8 b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse and first forward ratio. Forexample, the ratio step between the first and second forward ratios is1.50.

A powertrain 810, shown in FIG. 9 a, has the conventional engine andtorque converter 12, a planetary transmission 814, and the final drivemechanism 16. The engine and torque converter 12 are drivingly connectedwith the planetary transmission 814 through the input shaft 17. Theplanetary transmission 814 is drivingly connected with the final drivemechanism 16 through the output shaft 19. The planetary transmission 814includes a planetary gear arrangement 818 that has a first planetarygear set 820, a second planetary gear set 830, and a third planetarygear set 840.

The planetary gear set 820 includes a sun gear member 822, a ring gearmember 824, and a planet carrier assembly member 826. The planet carrierassembly member 826 includes a plurality of pinion gears 827 rotatablymounted on a carrier member 829 and disposed in meshing relationshipwith both the sun gear member 822 and the ring gear member 824.

The planetary gear set 830 includes a sun gear member 832, a ring gearmember 834, and a planet carrier assembly member 836. The planet carrierassembly member 836 includes a plurality of pinion gears 837 rotatablymounted on a carrier member 839 and disposed in meshing relationshipwith both the sun gear member 832 and the ring gear member 834.

The planetary gear set 840 includes a sun gear member 842, a ring gearmember 844, and a planet carrier assembly member 846. The planet carrierassembly member 846 includes a plurality of pinion gears 847 rotatablymounted on a carrier member 849 and disposed in meshing relationshipwith both the sun gear member 842 and the ring gear member 844.

The planetary gear arrangement 818 also includes seventorque-transmitting mechanisms 850, 852, 854, 856, 857, 858 and 859. Thetorque-transmitting mechanisms 850, 852, 854, 856 and 857 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 858 and 859 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member842, and the output shaft 19 is continuously connected with the sun gearmember 832. The sun gear member 822 is continuously connected with thering gear member 834 through the interconnecting member 870. Theinterconnecting member 870 may be one component or separate components.

The ring gear member 834 is selectively connectable with the ring gearmember 844 through the clutch 850. The planet carrier assembly member826 is selectively connectable with the ring gear member 844 through theclutch 852. The ring gear member 824 is selectively connectable with theplanet carrier assembly member 846 through the clutch 854. The planetcarrier assembly member 836 is selectively connectable with the ringgear member 844 through the clutch 856. The sun gear member 832 isselectively connectable with the planet carrier assembly member 846through the clutch 857. The sun gear member 822 is selectivelyconnectable with the transmission housing 860 through the brake 858. Theplanet carrier assembly member 826 is selectively connectable with thetransmission housing 860 through the brake 859.

The truth table shown in FIG. 9 b defines the torque-transmittingmechanism engagement sequence that provides the a reverse speed ratioand eight forward speed ratios, as well as an extra reverse speed ratio(Reverse′), shown in the truth table and available with the planetarygear arrangement 818. A sample of numerical values for the individualratios is also given in the truth table of FIG. 9 b. These numericalvalues have been calculated using the ring gear/sun gear tooth ratiosalso given by way of example in FIG. 9 b. The N_(R1)/S_(R1) value is thetooth ratio of the planetary gear set 820; the N_(R2)/S_(R2) value isthe tooth ratio of the planetary gear set 830; and the N_(R3)/S_(R3)value is the tooth ratio of the planetary gear set 840. It can bereadily recognized from the truth table that all of the single stepforward interchanges are of the single transition variety. Additionally,the torque-transmitting mechanisms 850, 854 and 859 remain engagedthrough the neutral condition, thus simplifying the forward/reverseinterchange. FIG. 9 b also describes the ratio steps between adjacentforward ratios and between the reverse (Reverse) and first forwardratio. For example, the ratio step between the first and second forwardratios is 1.42.

The powertrain 910, shown in FIG. 10 a, includes the conventional engineand torque converter 12, a planetary transmission 914, and theconventional final drive mechanism 16. The engine and torque converter12 are drivingly connected with the planetary transmission 914 throughthe input shaft 17. The planetary transmission 914 is drivinglyconnected with the final drive mechanism 16 through the output shaft 19.The planetary transmission 914 includes a planetary gear arrangement 918that has a first planetary gear set 920, a second planetary gear set930, and a third planetary gear set 940.

The planetary gear set 920 includes a sun gear member 922, a ring gearmember 924, and a planet carrier assembly member 926. The planet carrierassembly 926 includes a plurality of pinion gears 927 that are rotatablymounted on a carrier member 929 and disposed in meshing relationshipwith both the sun gear member 922 and the ring gear member 924.

The planetary gear set 930 includes a sun gear member 932, a ring gearmember 934, and a planet carrier assembly member 936. The planet carrierassembly member 936 includes a plurality of pinion gears 937 rotatablymounted on a carrier member 939 and disposed in meshing relationshipwith both the sun gear member 932 and the ring gear member 934.

The planetary gear set 940 includes a sun gear member 942, a ring gearmember 944, and a planet carrier assembly member 946. The planet carrierassembly member 946 includes a plurality of pinion gears 947 rotatablymounted on a carrier member 949 and disposed in meshing relationshipwith both the sun gear member 942 and the ring gear member 944.

The planetary gear arrangement 918 also includes seventorque-transmitting mechanisms 950, 952, 954, 956, 957, 958 and 959. Thetorque-transmitting mechanisms 950, 952, 954, 956 and 957 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 958 and 959 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member922, and the output shaft 19 is continuously connected with the ringgear member 944. The ring gear member 924 is continuously connected withthe planet carrier assembly member 936 through the interconnectingmember 970.

The planet carrier assembly member 936 is selectively connectable withthe sun gear member 942 through the clutch 950. The planet carrierassembly member 926 is selectively connectable with the ring gear member934 through the clutch 952. The planet carrier assembly member 926 isselectively connectable with the ring gear member 944 through the clutch954. The sun gear member 932 is selectively connectable with the sungear member 942 through the clutch 956. The ring gear member 934 isselectively connectable with the planet carrier assembly member 946through the clutch 957. The sun gear member 932 is selectivelyconnectable with the transmission housing 960 through the brake 958. Theplanet carrier assembly member 946 is selectively connectable with thetransmission housing 960 through the brake 959.

The truth table of FIG. 10 b describes the torque-transmitting mechanismengagement sequence utilized to provide a reverse (Reverse) speed ratioand eight forward speed ratios (as well as an extra reverse speed ratio(Reverse′), an extra second forward speed ratio (2′), an extra fifthforward speed ratio (5′), and an extra seventh forward speed ratio(7′)). The truth table also provides a set of examples for the ratiosfor each of the reverse and forward speed ratios. These numerical valueshave been determined utilizing the ring gear/sun gear tooth ratios givenin FIG. 10 b. The N_(R1)/S_(R1) value is the tooth ratio of theplanetary gear set 920; the N_(R2)/S_(R2) value is the tooth ratio ofthe planetary gear set 930; and the N_(R3)/S_(R3) value is the toothratio of the planetary gear set 940. As can also be determined from thetruth table of FIG. 10 b, each of the single step forward interchangesare of the single transition variety. Additionally, thetorque-transmitting mechanisms 950 and 959 remain engaged through theneutral condition, thus simplifying the forward/reverse interchange.

A powertrain 1010, shown in FIG. 11 a, includes the conventional engineand torque converter 12, a planetary transmission 1014, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1014 through theinput shaft 17. The planetary transmission 1014 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1014 includes a planetary gear arrangement 1018that has a first planetary gear set 1020, a second planetary gear set1030, and a third planetary gear set 1040.

The planetary gear set 1020 includes a sun gear member 1022, a ring gearmember 1024, and a planet carrier assembly member 1026. The planetcarrier assembly member 1026 includes a plurality of pinion gears 1027rotatably mounted on a carrier member 1029 and disposed in meshingrelationship with both the sun gear member 1022 and the ring gear member1024.

The planetary gear set 1030 includes a sun gear member 1032, a ring gearmember 1034, and a planet carrier assembly member 1036. The planetcarrier assembly member 1036 includes a plurality of pinion gears 1037rotatably mounted on a carrier member 1039 and disposed in meshingrelationship with both the sun gear member 1032 and the ring gear member1034.

The planetary gear set 1040 includes a sun gear member 1042, a ring gearmember 1044, and a planet carrier assembly member 1046. The planetcarrier assembly member 1046 includes a plurality of pinion gears 1047rotatably mounted on a carrier member 1049 and disposed in meshingrelationship with both the sun gear member 1042 and the ring gear member1044.

The planetary gear arrangement 1018 also includes seventorque-transmitting mechanisms 1050, 1052, 1054, 1056, 1057, 1058 and1059. The torque-transmitting mechanisms 1050, 1052, 1054, 1056, 1057and 1058 are rotating type torque-transmitting mechanisms, commonlytermed clutches. The torque-transmitting mechanism 1059 is a stationarytype torque-transmitting mechanism, commonly termed a brake or reactionclutch.

The input shaft 17 is continuously connected with the sun gear member1042, and the output shaft 19 is continuously connected with the ringgear member 1024. The sun gear member 1022 is continuously connectedwith the ring gear member 1034 through the interconnecting member 1070.The interconnecting member 1070 may be one component or separatecomponents.

The sun gear member 1022 is selectively connectable with the ring gearmember 1044 through the clutch 1050. The sun gear member 1032 isselectively connectable with the planet carrier assembly member 1046through the clutch 1052. The ring gear member 1024 is selectivelyconnectable with the planet carrier assembly member 1036 through theclutch 1054. The planet carrier assembly member 1036 is selectivelyconnectable with the ring gear member 1044 through the clutch 1056. Theplanet carrier assembly member 1026 is selectively connectable with thesun gear member 1042 through the clutch 1057. The planet carrierassembly member 1026 is selectively connectable with the planet carrierassembly member 1046 through the clutch 1058. The sun gear member 1032is selectively connectable with the transmission housing 1060 throughthe brake 1059.

The truth table shown in FIG. 11 b describes the engagement combinationsand the engagement sequence necessary to provide a reverse (Reverse)drive ratio and ten forward speed ratios, as well as an extra reversespeed ratio (Reverse′) and an extra tenth forward speed ratio (10′). Asample of the numerical values for the ratios is also provided in thetruth table of FIG. 11 b. These values are determined utilizing the ringgear/sun gear tooth ratios also given in FIG. 11 b. The N_(R1)/S_(R1)value is the tooth ratio for the planetary gear set 1020; theN_(R2)/S_(R2) value is the tooth ratio for the planetary gear set 1030;and the N_(R3)/S_(R3) value is the tooth ratio for the planetary gearset 1040. As shown in the truth table of FIG. 11 b, thetorque-transmitting mechanisms 1050, 1052 and 1059 remain engagedthrough the neutral condition, thus simplifying the forward/reverseinterchange. Also given in FIG. 11 b is a chart describing the stepratios between the adjacent forward speed ratios and the reverse(Reverse) to first forward speed ratio.

A powertrain 1110, shown in FIG. 12 a, includes the conventional engineand torque converter 12, a planetary transmission 1114, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1114 through theinput shaft 17. The planetary transmission 1114 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1114 includes a planetary gear arrangement 1118that has a first planetary gear set 1120, a second planetary gear set1130, and a third planetary gear set 1140.

The planetary gear set 1120 includes a sun gear member 1122, a ring gearmember 1124, and a planet carrier assembly member 1126. The planetcarrier assembly member 1126 includes a plurality- of pinion gears 1127rotatably mounted on a carrier member 1129 and disposed in meshingrelationship with both the sun gear member 1122 and the ring gear member1124.

The planetary gear set 1130 includes a sun gear member 1132, a ring gearmember 1134, and a planet carrier assembly member 1136. The planetcarrier assembly member 1136 includes a plurality of pinion gears 1137rotatably mounted on a carrier member 1139 and disposed in meshingrelationship with both the sun gear member 1132 and the ring gear member1134.

The planetary gear set 1140 includes a sun gear member 142, a ring gearmember 1144, and a planet carrier assembly member 1146. The planetcarrier assembly member 1146 includes a plurality of pinion gears 1147rotatably mounted on a carrier member 1149 and disposed in meshingrelationship with both the sun gear member 1142 and the ring gear member1144.

The planetary gear arrangement 1118 also includes seventorque-transmitting mechanisms 1150, 1152, 1154, 1156, 1157, 1158 and1159. The torque-transmitting mechanisms 1150, 1152, 1154, 1156, 1157and 1158 are rotating type torque-transmitting mechanisms, commonlytermed clutches. The torque-transmitting mechanism 1159 is a stationarytype torque-transmitting mechanism, commonly termed a brake or reactionclutch.

The input shaft 17 is continuously connected with the sun gear member1122, and the output shaft 19 is continuously connected with the ringgear member 1144. The ring gear member 1124 is continuously connectedwith the planet carrier assembly member 1136 through the interconnectingmember 1170. The interconnecting member 1170 may be one component orseparate components.

The planet carrier assembly member 1136 is selectively connectable withthe sun gear member 1142 through the clutch 1150. The sun gear member1122 is selectively connectable with the planet carrier assembly member1146 through the clutch 1152. The planet carrier assembly member 1126 isselectively connectable with the sun gear member 1132 through the clutch1154. The planet carrier assembly member 1126 is selectively connectablewith the planet carrier assembly member 1146 through the clutch 1156.The ring gear member 1134 is selectively connectable with the sun gearmember 1142 through the clutch 1157. The ring gear member 1144 isselectively connectable with the planet carrier assembly member 1146through the clutch 1158. The sun gear member 1132 is selectivelyconnectable with the transmission housing 1160 through the brake 1159.

The truth table shown in FIG. 12 b describes the engagement combinationsand the engagement sequence necessary to provide a reverse (Reverse)drive ratio and nine forward speed ratios, as well as an extra reversespeed ratio (Reverse′). A sample of the numerical values for the ratiosis also provided in the truth table of FIG. 12 b. The values aredetermined utilizing the ring gear/sun gear tooth ratios also given inFIG. 12 b. The N_(R1)/S_(R2) value is the tooth ratio of the planetarygear set 1120; the N_(R2)/S_(R2) value is the tooth ratio of theplanetary gear set 1130; and the N_(R3)/S_(R3) value is the tooth ratioof the planetary gear set 1140. As can also be determined from the truthtable of FIG. 12 b, the torque-transmitting mechanisms 1150 and 1159remains engaged through the neutral condition, thus simplifying theforward/reverse interchange. Also given in FIG. 12 b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse (Reverse) to first forward speed ratio. For example, stepratio between the first and second forward speed ratios is 1.49.

A powertrain 1210, shown in FIG. 13 a, includes the conventional engineand torque converter 12, a planetary transmission 1214, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1214 through theinput shaft 17. The planetary transmission 1214 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1214 includes a planetary gear arrangement 1218that has a first planetary gear set 1220, a second planetary gear set1230, and a third planetary gear set 1240.

The planetary gear set 1220 includes a sun gear member 1222, a ring gearmember 1224, and a planet carrier assembly member 1226. The planetcarrier assembly member 1226 includes a plurality of pinion gears 1227rotatably mounted on a carrier member 1229 and disposed in meshingrelationship with both the sun gear member 1222 and the ring gear member1224.

The planetary gear set 1230 includes a sun gear member 1232, a ring gearmember 1234, and a planet carrier assembly member 1236. The planetcarrier assembly member 1236 includes a plurality of pinion gears 1237rotatably mounted on a carrier member 1239 and disposed in meshingrelationship with both the sun gear member 1232 and the ring gear member1234.

The planetary gear set 1240 includes a sun gear member 1242, a ring gearmember 1244, and a planet carrier assembly member 1246. The planetcarrier assembly member 1246 includes a plurality of pinion gears 1247rotatably mounted on a carrier member 1249 and disposed in meshingrelationship with both the sun gear member 1242 and the ring gear member1244.

The planetary gear arrangement 1218 also includes seventorque-transmitting mechanisms 1250, 1252, 1254, 1256, 1257, 1258 and1259. The torque-transmitting mechanisms 1250, 1252, 1254 and 1256 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanisms 1257, 1258 and 1259 are stationarytype torque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the sun gear member1242, and the output shaft 19 is continuously connected with the ringgear member 1224. The planet carrier assembly member 1226 iscontinuously connected with the planet carrier assembly member 1236through the interconnecting member 1270

The planet carrier assembly member 1236 is selectively connectable withthe sun gear member 1242 through the clutch 1250. The sun gear member1222 is selectively connectable with the ring gear member 1234 throughthe clutch 1252. The ring gear member 1234 is selectively connectablewith the planet carrier assembly member 1246 through the clutch 1254.The sun gear member 1222 is selectively connectable with the ring gearmember 1244 through the clutch 1256. The sun gear member 1232 isselectively connectable with the transmission housing 1260 through thebrake 1257. The planet carrier assembly member 1246 is selectivelyconnectable with the transmission housing 1260 through the brake 1258.The ring gear member 1244 is selectively connectable with thetransmission housing 1260 through the brake 1259.

The truth table shown in FIG. 13 b described the engagement combinationsand the engagement sequence necessary to provide a reverse drive ratioand nine forward speed ratios (as well as an extra second forward speedratio (2′)). A sample of the numerical values for the ratios is alsoprovided in the truth table of FIG. 13 b. These values are determinedutilizing the ring gear/sun gear tooth ratios also given in FIG. 13 b.The N_(R1)/S_(R1) value is the tooth ratio of the planetary gear set1220; the N_(R2)/S_(R2) value is the tooth ratio of the planetary gearset 1230; and the N_(R3)/S_(R3) value is the tooth ratio of theplanetary gear set 1240. As can be determined from the truth table ofFIG. 13 b, each of the single step forward interchanges is of the singletransition variety. Additionally, the torque-transmitting mechanisms1252 and 1257 remain engaged through the neutral condition, thussimplifying the forward/reverse interchange. Also given in FIG. 13 b isa chart describing the step ratios between the adjacent forward speedratios and the reverse to first forward speed ratio.

A powertrain 1310, shown in FIG. 14 a, includes the conventional engineand torque converter 12, a planetary transmission 1314, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1314 through theinput shaft 17. The planetary transmission 1314 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1314 includes a planetary gear arrangement 1318that has a first planetary gear set 1320, a second planetary gear set1330, and a third planetary gear set 1340.

The planetary gear set 1320 includes a sun gear member 1322, a ring gearmember 1324, and a planet carrier assembly member 1326. The planetcarrier assembly member 1326 includes a plurality of pinion gears1327,rotatably mounted on a carrier member 1329 and disposed in meshingrelationship with both the sun gear member 1322 and the ring gear member1324.

The planetary gear set 1330 includes a sun gear member 1332, a ring gearmember 1334, and a planet carrier assembly member 1336. The planetcarrier assembly member 1336 includes a plurality of pinion gears 1337rotatably mounted on a carrier member 1339 and disposed in meshingrelationship with both the sun gear member 1332 and the ring gear member1334.

The planetary gear set 1340 includes a sun gear member 1342, a ring gearmember 1344, and a planet carrier assembly member 1346. The planetcarrier assembly member 1346 includes a plurality of pinion gears 1347rotatably mounted on a carrier member 1349 and disposed in meshingrelationship with both the sun gear member 1342 and the ring gear member1344.

The planetary gear arrangement 1318 also includes seventorque-transmitting mechanisms 1350, 1352, 1354, 1356, 1357, 1358 and1359. The torque-transmitting mechanisms 1350, 1352, 1354 and 1356 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 1359 is a stationary typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches.

The input shaft 17 is continuously connected with the planet carrierassembly member 1326, and the output shaft 19 is continuously connectedwith the planet carrier assembly member 1346. The sun gear member 1322is continuously connected with the sun gear member 1332 through theinterconnecting member 1370.

The sun gear member 1332 is selectively connectable with the ring gearmember 1344 through the clutch 1350. The ring gear member 1324 isselectively connectable with the planet carrier assembly member 1336through the clutch 1352. The ring gear member 1334 is selectivelyconnectable with the sun gear member 1342 through the clutch 1354. Theplanet carrier assembly member 1336 is selectively connectable with thesun gear member 1342 through the clutch 1356. The ring gear member 1324is selectively connectable with the transmission housing 1360 throughthe brake 1357. The ring gear member 1334 is selectively connectablewith the transmission housing 1360 through the brake 1358. The ring gearmember 1344 is selectively connectable with the transmission housing1360 through the brake 1359.

The truth table shown in FIG. 14 b describes the engagement combinationsand the engagement sequence necessary to provide a reverse drive ratioand ten forward speed ratios, as well-as an extra second forward speedratio (2′), an extra sixth forward speed ratio (6′), and an extra eighthforward speed ratio (8′). As sample of the numerical values for theratios is also provided in the truth table of FIG. 14 b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 14 b. The N_(R1)/S_(R1) value is the tooth ratio of theplanetary gear set 1320; the N_(R2)/S_(R2) value is the tooth ratio ofthe planetary gear set 1330; and the N_(R3)/S_(R3) value is the toothratio of the planetary gear set 1340. As can also be determined from thetruth table of FIG. 14 b, each of the single step forward interchangesis of the single transition variety. Additionally, thetorque-transmitting mechanisms 1352 and 1359 remain engaged through theneutral condition, thus simplifying the forward/reverse interchange.Also given in FIG. 14 b is a chart describing the step ratios betweenthe adjacent forward speed ratios and the reverse to first forward speedratio.

A powertrain 1410, shown in FIG. 15 a, includes the conventional engineand torque converter 12, a planetary transmission 1414, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1414 through theinput shaft 17. The planetary transmission 1414 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1414 includes a planetary gear arrangement 1418that has a first planetary gear set 1420, a second planetary gear set1430, and a third planetary gear set 1440.

The planetary gear set 1420 includes a sun gear member 1422, a ring gearmember 1424, and a planet carrier assembly member 1426. The planetcarrier assembly member 1426 includes a plurality of pinion gears 1427rotatably mounted on a carrier member 1429 and disposed in meshingrelationship with both the sun gear member 1422 and the ring gear member1424.

The planetary gear set 1430 includes a sun gear member 1432, a ring gearmember 1434, and a planet carrier assembly member 1436. The planetcarrier assembly member 1436 includes a plurality of pinion gears 1437rotatably mounted on a carrier member 1439 and disposed in meshingrelationship with the sun gear member 1432. Pinion gears 1438 aredisposed in meshing relationship with both the ring gear member 1434 andthe pinion gears 1437.

The planetary gear set 1440 includes a sun gear member 1442, a ring gearmember 1444, and a planet carrier assembly member 1446. The planetcarrier assembly member 1446 includes a plurality of pinion gears 1447rotatably mounted on a carrier member 1449 and disposed in meshingrelationship with both the sun gear member 1442 and the ring gear member1444.

The planetary gear arrangement 1418 also includes seventorque-transmitting mechanisms 1450, 1452, 1454, 1456, 1457, 1458 and1459. The torque-transmitting mechanisms 1450, 1452, 1454, 1456 and 1457are rotating type torque-transmitting mechanisms, commonly termedclutches. The torque-transmitting mechanisms 1158 and 1159 arestationary type torque-transmitting mechanisms, commonly termed brakesor reaction clutches.

The input shaft 17 is continuously connected with the sun gear member1422, and the output shaft 19 is continuously connected with the ringgear member 1444. The ring gear member 1424 is continuously connectedwith the ring gear member 1434 through the interconnecting member 1470.The interconnecting member 1470 may be one component or separatecomponents.

The ring gear member 1424 is selectively connectable with the sun gearmember 1442 through the clutch 1450. The sun gear member 1422 isselectively connectable with the planet carrier assembly member 1446through the clutch 1452. The planet carrier assembly member 1426 isselectively connectable with the planet carrier assembly member 1446through the clutch 1454. The planet carrier assembly member 1436 isselectively connectable with the sun gear member 1442 through the clutch1456. The planet carrier assembly member 1436 is selectively connectablewith the planet carrier assembly member 1446 through the clutch 1457.The planet carrier assembly member 1426 is selectively connectable withthe transmission housing 1460 through the brake 1458. The sun gearmember 1432 is selectively connectable with the transmission housing1460 through the brake 1459.

The truth table shown in FIG. 15 b describes the engagement combinationsand the engagement sequence necessary to provide a reverse (Reverse)drive ratio and ten forward speed ratios (as well as an extra reversespeed ratio (Reverse′) and an extra first sixth speed ratio (6′)). Asample of the numerical values for the ratios is also provided in thetruth table of FIG. 15 b. These values are determined utilizing the ringgear/sun gear tooth ratios also given in FIG. 15 b. The N_(R1)/S_(R1)value is the tooth ratio of the planetary gear set 1420; theN_(R2)/S_(R2) value is the tooth ratio of the planetary gear set 1430;and the N_(R3)/S_(R3) value is the tooth ratio of the planetary gear set1440. As can also be determined from the truth table of FIG. 15 b, eachof the single step forward interchanges is of the single transitionvariety. Additionally, the torque-transmitting mechanisms 1450, 1456 and1458 remain engaged through the neutral condition, thus simplifying theforward/reverse interchange. Also given in FIG. 15 b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse (Reverse) to first forward speed ratio.

While the best modes for carrying out the invention have been describedin detail, those familiar with the art to which this invention relateswill recognize various alternative designs and embodiments forpracticing the invention within the scope of the appended claims.

1. A multi-speed transmission comprising: an input shaft; an outputshaft; first, second and third planetary gear sets each having first,second and third members; said input shaft being continuouslyinterconnected with a member of said planetary gear sets, and saidoutput shaft being continuously interconnected with another member ofsaid planetary gear sets; an interconnecting member continuouslyinterconnecting said first member of said first planetary gear set withsaid first member of said second planetary gear set; a firsttorque-transmitting mechanism selectively interconnecting a first memberof said third planetary gear set with a member of said first planetarygear set; a second torque-transmitting mechanism selectivelyinterconnecting a second member of said third planetary gear set with amember of said first or second planetary gear set; a thirdtorque-transmitting mechanism selectively interconnecting a third memberof said third planetary gear set with a member of said first or secondplanetary gear set; a fourth torque-transmitting mechanism selectivelyinterconnecting a member of said first or second planetary gear set withanother member of said first, second or third planetary gear set; afifth torque-transmitting mechanism selectively interconnecting a memberof said first, second or third planetary gear set with a stationarymember; a sixth torque-transmitting mechanism selectivelyinterconnecting a member of said second or third planetary gear set withanother member of said first, second or third planetary gear set, orwith said stationary member; and a seventh torque-transmitting mechanismselectively interconnecting a member of said first or second planetarygear set with another member of said first, second or third planetarygear set, or with said stationary member; said torque-transmittingmechanisms being engaged in combinations of four to establish at leasteight forward speed ratios and at least one reverse speed ratio betweensaid input shaft and said output shaft.
 2. The transmission defined inclaim 1, wherein said first, second, third and fourthtorque-transmitting mechanisms comprise clutches, and said fifth, sixthand seventh torque-transmitting mechanisms comprise brakes.
 3. Thetransmission defined in claim 1, wherein said first, second, third,fourth and seventh torque-transmitting mechanisms comprise clutches, andsaid fifth and sixth torque-transmitting mechanisms comprise brakes. 4.The transmission defined in claim 1, wherein said first, second, third,fourth, sixth and seventh torque-transmitting mechanism compriseclutches and said fifth torque-transmitting mechanism comprises a brake.5. The transmission defined in claim 1, wherein planet carrier assemblymembers of each of said planetary gear sets are single-pinion carriers.6. The transmission defined in claim 1, wherein at least one planetcarrier assembly member of said planetary gear sets is a double-pinioncarrier.
 7. A multi-speed transmission comprising: an input shaft; anoutput shaft; a planetary gear arrangement having first, second andthird planetary gear sets, each planetary gear set having first, secondand third members; said input shaft being continuously interconnectedwith a member of said planetary gear sets, and said output shaft beingcontinuously interconnected with another member of said planetary gearsets; an interconnecting member continuously interconnecting said firstmember of said first planetary gear set with said first member of saidsecond planetary gear set; and seven torque-transmitting mechanisms forselectively interconnecting said members of said planetary gear setswith a stationary member or with other members of said planetary gearsets, said seven torque-transmitting mechanisms being engaged incombinations of four to establish at least eight forward speed ratiosand at least one reverse speed ratio between said input shaft and saidoutput shaft.
 8. The transmission defined in claim 8, wherein a first ofsaid seven torque-transmitting mechanisms is operable for selectivelyinterconnecting said first member of said third planetary gear set witha member of said first planetary gear set.
 9. The transmission definedin claim 8, wherein a second of said seven torque-transmittingmechanisms is operable for selectively interconnecting said secondmember of said third planetary gear set with a member of said first orsecond planetary gear set.
 10. The transmission defined in claim 8,wherein a third of said seven torque-transmitting mechanisms is operablefor selectively interconnecting said third member of said thirdplanetary gear set with a member of said first or second planetary gearset.
 11. The transmission defined in claim 8, wherein a fourth of saidseven torque-transmitting mechanisms is operable for selectivelyinterconnecting a member of said first or second planetary gear set withanother member of said first, second or third planetary gear set. 12.The transmission defined in claim 8, wherein a fifth of said seventorque-transmitting mechanisms is operable for selectivelyinterconnecting a member of said first, second or third planetary gearset with said stationary member.
 13. The transmission defined in claim8, wherein a sixth of said seven torque-transmitting mechanisms isoperable for selectively interconnecting a member of said second orthird planetary gear set with another member of said first, second orthird planetary gear set, or with said stationary member.
 14. Thetransmission defined in claim 8, wherein a seventh of said seventorque-transmitting mechanisms is operable for selectivelyinterconnecting a member of said first or second planetary gear set withanother member of said first, second or third planetary gear set, orwith said stationary member.
 15. The transmission defined in claim 8,wherein planet carrier assembly members of each of said planetary gearsets are single-pinion carriers.
 16. The transmission defined in claim8, wherein at least one planet carrier assembly member of said planetarygear sets is a double-pinion carrier.